US6000467A - Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes - Google Patents

Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes Download PDF

Info

Publication number
US6000467A
US6000467A US09/087,016 US8701698A US6000467A US 6000467 A US6000467 A US 6000467A US 8701698 A US8701698 A US 8701698A US 6000467 A US6000467 A US 6000467A
Authority
US
United States
Prior art keywords
tube
cross
unit passages
outermost
circular
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US09/087,016
Other languages
English (en)
Inventor
Kazumi Tokizaki
Yutaka Higo
Nobuaki Go
Shigeharu Ichiyanagi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Resonac Holdings Corp
Original Assignee
Showa Aluminum Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=26411135&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=US6000467(A) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Showa Aluminum Corp filed Critical Showa Aluminum Corp
Assigned to SHOWA ALUMINUM CORPORATION reassignment SHOWA ALUMINUM CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GO, NOBUAKI, HIGO, YUTAKA, ICHIYANAGI, SHIGEHARU, TOKIZAKI, KAZUMI
Priority to US09/419,519 priority Critical patent/US6289981B1/en
Application granted granted Critical
Publication of US6000467A publication Critical patent/US6000467A/en
Assigned to SHOWA DENKO K.K. reassignment SHOWA DENKO K.K. MERGER (SEE DOCUMENT FOR DETAILS). Assignors: SHOWA ALUMINUM CORPORATION
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/04—Reinforcing means for conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/16—Safety or protection arrangements; Arrangements for preventing malfunction for preventing leakage

Definitions

  • the present invention relates to a multi-bored flat tube for use in a heat-exchanger and, more particulary, to a multi-bored flat tube made of a metal such as an aluminum for use in a condenser for an air conditioner.
  • the present invention further relates to a heat exchanger including the multi-bored flat tubes.
  • FIGS. 14(A)-(C) show cross-sectional views of a conventional multi-bored flat tube of this kind.
  • the multi-bored flat tube 51 is made by extruding an aluminum.
  • the tube 51 has a peripheral wall 52 having an elongated circular cross-sectional shape and a plurality of divisional wall 53, 53a connecting flat wall portions 52a, 52a of the peripheral wall 52.
  • the divisional walls 53 divide an inside space of the tube 51 to form a plurality of unit passages 54, 55 arranged in a lateral direction of the tube 51.
  • Each divisional wall 53, 53a has a constant thickness along the height thereof so that a contact area with the heat exchanging medium can be enlarged, thereby enhancing the heat exchanging performance of the tube 51.
  • the tube 51 includes outermost unit passages 54, 54 and intermediate unit passages 55 located between the outermost unit passages 54, 54.
  • Each intermediate passage 55 has a rectangular cross-sectional shape
  • each outermost unit passage 54 has a semi-circular cross-sectional shape at a lateral outside portion and a rectangular cross-sectional shape at lateral inside portion.
  • each portion of the tube 51 i.e., the peripheral wall 52 and the divisional walls 53, 53a, are formed to be as thin as possible for the purpose of lightening the weight of the tube 51.
  • Japanese unexamined Utility Model Publication No. S60-196181 and Japanese examined Utility Model Publication No. H3-45034 disclose a tube having unit passages with inner fins formed on an inner surface of each unit passage to enlarge a contact area with the heat exchanging medium for the purpose of enhancing the heat exchanging performance.
  • a tube 52 has a plurality of inner fins 62 formed on the inner surface of the unit passages 54, 55 surrounded by the peripheral wall 52 and the divisional walls 53, 53a.
  • Each fin 62 has a triangular cross-sectional shape and extends in the longitudinal direction of the tube 61.
  • Japanese unexamined Patent Publication No. H5-215482 discloses another type of heat exchanging multi-bored flat tube.
  • the tube has a plurality of unit passages each having a round cross-sectional shape for the purpose of equalizing the flow speed of the heat exchanging medium and lowering the flow resistance of the heat exchanging medium in each unit passage.
  • FIGS. 14 and 15, the reference numeral 57 denotes a corrugate fin interposed between the adjacent tubes 61.
  • a stress caused by an inner pressure of the heat exchanging medium passing through the tube is concentrated on connecting portions between the divisional wall 53, 53a and the peripheral wall 52.
  • the lateral middle portion of the tube 51, 61 can withstand such a stress because the flat wall portions 52a of the peripheral wall 52 are supported and reinforced by the corrugate fins 57, 57.
  • the lateral end portions of the tube 51, 61 are not strong enough to withstand such a stress because reinforcing effects obtained by the corrugate fins 57, 57 are not enough. Therefore, such a stress tends to be concentrated on the connecting portions between the outermost dividing wall 53a and the peripheral wall 52 to cause a breakage.
  • the above-mentioned tubes used in a condenser mounted in an automobile may sometimes be damaged and cause leakage of the heat exchanging medium when a stone, or the like, hits the tube while the automobile is moving.
  • a flow resistance of heat exchanging medium passing through the unit passage can be decreased and the pressure resistance can be improved.
  • upper and lower portions of each dividing wall are thicker than the middle portion thereof, which requires larger amount of material for forming the tube, thereby increasing the manufacturing costs.
  • a heat transferring area of the circular cross-sectional unit passage is smaller than that of the rectangular cross-sectional unit passage, resulting in a lower heat exchanging efficiency.
  • the present invention has been made to overcome the disadvantages in the conventional multi-bored flat tube for use in a heat exchanger as described above.
  • An object of the present invention is to provide a multi-bored flat tube having an improved strength against a stone or the like which hits the tube, and an excellent heat exchanging performance by keeping a large contact area with a heat exchanging medium.
  • Another object of the present invention is to provide a heat exchanger including the above-mentioned flat tubes.
  • a multi-bored flat tube for use in a heat exchanger comprising:
  • peripheral wall including flat wall portions facing each other at a certain distance and sidewall portions connecting lateral ends of the flat wall portions;
  • the plurality of unit passages include outermost unit passages located at both lateral ends of the tube and intermediate unit passages located between the outermost unit passages.
  • Each of the outermost unit passages has a circular-based inner surface in cross-section, and each of the intermediate unit passages has a non-circular inner surface in cross-section.
  • the outermost unit passages have a circular-based inner surface in cross-section, a stress concentration on connecting portions between the outermost dividing wall and the peripheral wall can be decreased. Accordingly, a high pressure resistance can be obtained throughout the tube.
  • a high pressure resistance can be obtained by the structure even at both lateral ends of the tube where reinforcing effect by the outer fins is not enough.
  • the outermost unit passage when the outermost unit passage is designed to have a circular cross-sectional shape, an inner pressure of the heat exchanging medium passing through the passage acts on the inner surface of the passages equally in the circumferential direction thereof. Therefore, a higher pressure resistance can be obtained. This effect is remarkable when the outermost unit passage is designed to have a perfect circular shape. Furthermore, since the outermost unit passage is designed to have a circular-based inner surface in cross-section, a stress concentration on connecting portions between the outermost dividing wall and the peripheral wall can be reduced even when a small article such as a stone hits the tube. Consequently, the peripheral wall at the connecting portions can be prevented from being damaged, resulting in superior breaking strength against an outside stress caused when small article such as a stone hits the tube.
  • the outermost unit passage may have a circumferentially smooth curved shape in cross-section.
  • This circumferentially smooth curved shape in cross-section includes various kinds of circular shapes such as a perfect circular shape, an elliptical shape, an elongated circular shape, or the like.
  • the outermost unit passage may have a star-like shape in cross-section, i.e., a circular-based cross-sectional shape having a plurality of inner fins extending in a longitudinal direction of the tube.
  • the contact area with the refrigerant can be enlarged, thereby improving the heat exchange performance.
  • Each of the intermediate unit passages is designed to have a non-circular inner surface in cross-section. This can prevent the thickness of upper and lower portions of the dividing wall from being thickened as compared to an intermediate unit passage having a circular-based inner surface, which results in a decreased amount of materials, thereby decreasing the weight and costs of the tube.
  • a larger contact area with the heat exchanging medium can be obtained as compared to an intermediate unit passage having a circular inner surface, which in turn can obtain a high heat exchanging performance.
  • non-circular means other than circular and includes any kinds of shape, such as a triangular shape, a square shape, a trapezoidal shape, a star-like shape as well as a shape having uneven inside surfaces thereof.
  • the intermediate unit passage adjacent to the outermost unit passage may have a semi-circular inner surface at the outermost unit passage side. This can decrease a stress concentration on the connecting portions between the outermost dividing wall and the peripheral wall to improve the strength, whereby the peripheral wall at the connecting portions can effectively be prevented from being broken.
  • the sidewall portion may have a rounded shape in cross-section and may be formed relatively thicker than the flat wall portions. This can prevent the sidewall portion from being broken or deformed when a small article such as a stone hits the sidewall portion.
  • the thickness of the flat wall portions is kept relatively thinner, an optimal heat transmission performance can be maintained and an increase in the weight can be avoided, resulting in a light-weight heat exchanger. Further, the structure does not cause an increased pressure loss of the heat exchanging medium.
  • the intermediate unit passages may have a square, triangular, or trapezoidal shapes in cross-section. In the case of intermediate unit passages having triangular or trapezoidal shapes, it is preferable to invert the orientation of adjacent passages in order to have as many unit passages as possible.
  • the intermediate unit passage can have a large heat transmission area as compared with a passage having a circular shape in cross-section, thereby improving the heat-exchanging efficiency.
  • the intermediate unit passages may also have a star-like shape in cross-section, that is a circular-based shape having a plurality of inner fins extending in a longitudinal direction of the tube.
  • a star-like shape in cross-section that is a circular-based shape having a plurality of inner fins extending in a longitudinal direction of the tube.
  • a multi-bored flat tube for use in a heat-exchanger comprising;
  • peripheral wall including flat wall portions facing with each other at a certain distance and sidewall portions connecting ends of the flat wall portions;
  • the plurality of unit passages include outermost unit passages located at both lateral ends of the tube and intermediate unit passages located between both the outermost unit passages, and
  • each of the outermost unit passages has a circular-based inner surface in cross-section
  • each of the intermediate unit passages has a modified inner surface in cross-section
  • the outermost unit passages are designed to have a circular-based inner surface in cross-section, a stress concentration on the connecting portion between the outermost dividing wall and the peripheral wall can be reduced.
  • a high performance of pressure resistance can be obtained throughout the tube, and a superior breaking strength against an outside stress caused when a small article such as a stone hits the tube can be obtained.
  • each of the intermediate unit passages is designed to have a modified cross-sectional shape. This can prevent the thickness of upper and lower portions of the dividing wall from being thickened as compared to an intermediate unit passage having a circular inner surface in cross-section, which results in a decreased amount of material, thereby decreasing the weight and costs of the tube.
  • a larger contact area with the heat exchanging medium can be obtained as compared to an intermediate unit passage having a circular inner surface in cross-section, which in turn can obtain a high heat exchanging performance.
  • a heat-exchanger having the above-mentioned multi-bored flat tube can improve a breaking strength against a small article such as a stones which hits the tube, and can maintain a high heat transmission performance and a low pressure loss.
  • FIGS. 1A and 1B show a tube of an embodiment according to the present invention, wherein FIG. 1A is a cross-sectional view thereof, and FIG. 1B is an enlarged cross-sectional view of the lateral end portion thereof.
  • FIG. 2A is a part of cross-sectional view of a heat exchanger core including the tubes and fins
  • FIG. 2B is an enlarged cross-sectional view of the lateral end portion thereof against which a stone hits.
  • FIGS. 3A and 3B show a heat exchanger, wherein FIG. 3A is a front view thereof, and FIG. 3B is a top plan view thereof.
  • FIG. 4 is a graph showing examination results of the strength.
  • FIG. 5 is a graph showing examination results of the radiation amount.
  • FIG. 6 is a graph showing examination results of the pressure loss of the heat exchanging medium.
  • FIGS. 7A and 7B show a second embodiment of the tube according to the present invention, wherein FIG. 7A is a cross-sectional view of the tube, and FIG. 7B is an enlarged cross-sectional view of the lateral end portion thereof.
  • FIG. 8 is a cross-sectional view of a third embodiment of the tube according to the present invention.
  • FIG. 9 is a cross-sectional view of a forth embodiment of the tube according to the present invention.
  • FIGS. 10A and 10B show a fifth embodiment of the tube according to the present invention, wherein FIG. 10A is a cross-sectional view of the tube, and FIG. 10B is an enlarged cross-sectional view of the lateral end portion thereof.
  • FIG. 11A is a part of cross-sectional view of a heat exchanger core including the tubes and fins
  • FIG. 11B is an enlarged cross-sectional view of the lateral end portion thereof.
  • FIGS. 12A and 12B show a sixth embodiment of the tube according to the present invention, wherein FIG. 12A is a cross-sectional view thereof, and FIG. 12B is an enlarged cross-sectional view of the lateral end portion thereof.
  • FIGS. 13A and 13B show a seventh embodiment of the tube according to the present invention, wherein FIG. 13A is a cross-sectional view thereof, and FIG. 13B is an enlarged cross-sectional view of the lateral end portion thereof.
  • FIGS. 14A-14C show related art, wherein FIG. 14A is a cross-sectional view of a conventional tube, FIG. 14B is a partial cross-sectional view of a heat exchanger core including the tubes and fins, and FIG. 14C is an enlarged partial cross-sectional view of the tube to which a stone hit.
  • FIGS. 15A-15B show other related art, wherein FIG. 15A is a cross-sectional view of a partial cross-sectional view of a heat exchanger core including the tubes and fins, and FIG. 15B is an enlarged partial cross-sectional view thereof.
  • the multi-bored flat tube for use in a heat exchanger of the embodiment and a heat exchanger including the tubes are preferably used as a condenser for an automobile air conditioner.
  • FIG. 3 shows a heat exchanger of a so-called multi-flow type that includes a plurality of multi-bored flat tubes 1 each having a certain length, fins 2 interposed between the tubes 1, and a pair of hollow headers 3, 3 to which the ends of the tubes 1 are connected.
  • Each header 3 is divided by a partition 4 into upper and lower chambers.
  • a heat exchanging medium flows into the left hand header 3 through an inlet 5 connected to the upper portion of the header, passes through the tubes 1 in a zigzag manner, and flows out of the right hand header 3 through an outlet 6 connected to the lower portion of the header 3.
  • FIGS. 1 and 2 show a multi-bored flat tube 1 of the first embodiment used in the above-mentioned heat exchanger.
  • the tube 1 is an aluminum extruded article.
  • the peripheral wall 7 is formed to have an elongated circular cross-sectional shape.
  • a plurality of divisional walls 8 are provided in the tube 1 to form a plurality of unit passages 11, 11b, 11a arranged in the lateral direction of the tube 1.
  • the divisional walls 8 connect flat wall portions 9, 9 of the peripheral wall 7 faced with each other at a certain distance.
  • This tube 1 has rounded sidewall portions 10, 10 at the lateral end portions of the tube.
  • the sidewall portion 10 is formed to be thicker than the flat wall portion 9.
  • the maximum thickness t2 of the sidewall portion 10 can be designed to be 0.7 mm where the thickness t1 of the flat wall portion 9 is 0.35 mm.
  • each of the outermost unit passages 11a, 11a is formed to be a circumferentially smooth curved shape in cross-section.
  • the unit passage 11a is formed to be an elongated circular cross-sectional shape, but it may be formed to be an elliptical shape or a perfect circular shape.
  • Each intermediate unit passage 11b adjacent to the outermost unit passage 11a, i.e., the second passage 11b from the lateral end of the tube 1, has a rounded, or semicircular, inner surface at the outermost unit passage side and a rectangular inner surface at the other side.
  • each radius curvature R of the curved inner surfaces 12, 12, 12, 12 located at connecting portions between the outermost dividing wall 8 and the flat wall portions 9 is preferably designed to be approximately half of the height h of the unit passages 11.
  • the fin 2 is an aluminum corrugate fin. As shown in FIG. 2A, the fin 2 is disposed between adjacent tubes 1, 1 such that one lateral end of the fin 2 protrudes from one lateral end of the tube 1 toward leeward side.
  • the width of the fin 2 is the same as that of the tube 1 and, therefore, the other lateral end of the fin 2 is indented from the other lateral end of the tube 1 at rearward side.
  • the width of the fin 2 may be designed to be larger than that of the tube 1 so that one lateral end of the fin 2 protrudes from one lateral end of the tube 1 toward windward side and the other lateral end is not indented from the other lateral end of the tube 1 at rearward side.
  • the heat exchanger When the above-mentioned heat exchanger is used as a condenser for an automobile air conditioner, the heat exchanger may be hit by a stone passed through a radiator grill of the automobile. In this case, however, the rounded sidewall portion 10 is prevented from being destroyed by the stone because the thickness of the rounded sidewall portion 10 at the windward side is larger than that of the flat wall portion 9. Further, the rounded sidewall portion 10 is also prevented from being heavily deformed by the stone, and a stress concentration on connecting portions between the outermost dividing wall 8 and the flat wall portion 9 is decreased due to the stress concentration decreasing effect of the curved inner surfaces 12, 12, 12, 12, 12, which prevents the peripheral wall 7 at the connecting portions from being damaged.
  • FIG. 2B shows a stone hitting the rounded sidewall portion 10.
  • the thicknesses of the flat wall portions 9, 9 are kept relatively thinner, an optimal heat transmission performance can be maintained and a weight increase can be decreased, resulting in a light-weight heat exchanger. Further, the structure does not cause an increase in the pressure loss of the heat exchanging medium.
  • the fins 2 can also receive a stone to protect the tubes 1.
  • a condenser C1 having tubes 1 of the present invention shown in FIG. 1A and fins 2 interposed between adjacent tubes was prepared. One lateral end of the fin 2 protruded from one lateral end of the tube 1 toward windward side.
  • a condenser C2 having the tubes 1 and fins 2 interposed between adjacent tubes was prepared. One lateral end of the fin 2 did not protrude from one lateral end of the tube 1 toward windward side.
  • a condenser C3 having the conventional tubes 51 shown in FIG. 14 and fins 57 interposed between adjacent tubes was prepared. One lateral end of the fin 57 protruded from one lateral end of the tube 51 toward windward side.
  • a condenser C4 having the conventional tubes 51 and fins 57 interposed between adjacent tubes was prepared. One lateral end of the fin 57 did not protrude from one lateral end of the tube 57 toward windward side.
  • These four condensers C1, C2, C3, C4 were laid down and various sizes of steal weights were dropped from various heights on the condensers. Each steal weight had a size smaller than a distance between the adjacent tubes of the condensers. The results are shown in a graph shown in FIG. 4. In the graph, the vehicle velocity corresponds to the falling velocity of the weight just before the weight contacts the condenser.
  • the tube 1 according to the present invention can be prevented from being deformed or broken by a stone as compared to the conventional tube 51. Further, a lateral end of the fin 2 protruding toward the windward side can effectively prevent a tube from being deformed or broken.
  • the heat radiation rate and the pressure loss of the heat exchanging medium were also measured for each condenser. The results are shown in FIGS. 5 and 6. From the results, it was confirmed that the heat radiation rate and the pressure loss of the condensers C1 and C2 were as good as those of the conventional condensers C3 and C4.
  • FIG. 7 shows a second embodiment of a multi-bored flat tube according to the present invention. This embodiment differs from the first embodiment only in that the second unit passages 11b, 11b from lateral ends of the tube 1 are also formed to have a rectangular cross-sectional shape.
  • each of the outermost unit passages 11a, 11a is formed to have a circumferentially smooth curved shape in cross-section, a stress concentration on connecting portions between the outermost dividing wall 8 and the flat wall portion 9 decreases due to the stress concentration decreasing effect of the curved inner surfaces 12, 12, which prevents the peripheral wall 7 at the connecting portions from being destroyed.
  • each of the intermediate unit passages 11 is formed to have a rectangular shape in cross-section, the thickness of each portion can be thinner, thereby lightening the weight of the tube 1, resulting in a light weight heat exchanger. Further, the heat exchanging performance can be improved by increasing the contact area with a heat exchanging medium, as compared to a tube having intermediate unit passages each having a round shape in cross-section.
  • FIG. 8 shows a third embodiment of a multi-bored slat tube according to the present invention.
  • all intermediate unit passages 11 are formed to have a triangular cross-sectional shape, respectively.
  • the adjacent unit passages 11, 11 are disposed upside down (i.e., inverted).
  • the thickness of each rounded sidewall portion 10 located at the lateral end of the tube 1 is approximately the same as that of the flat wall portion 9.
  • each of the outermost unit passages 11a, 11a is formed to have a circumferentially smooth curved shape in cross-section. Therefore, a stress concentration on connecting portions between the outermost dividing wall 8 and the flat wall portion 9 is decreased due to the stress concentration decreasing effect of the curved inner surfaces 12, 12, which prevents the peripheral wall 7 at the connecting portions from being damaged.
  • each intermediate unit passage 11 has a triangular cross-sectional shape, the thickness of each portion can be thinner, thereby lightening the weight of the tube 1, resulting in a light weight heat exchanger, as in the same manner in the first and second embodiments. Further, the heat exchanging performance can be improved by the large contact area with a heat exchanging medium, as compared to a tube having intermediate unit passages each having a round shape in cross-section.
  • FIG. 9 shows a fourth embodiment of a multi-bored flat tube according to the present invention.
  • all intermediate unit passages 11 are formed to have a trapezoidal cross-sectional shape, respectively.
  • the adjacent unit passages 11, 11 are again disposed upside down.
  • the thickness of each rounded sidewall portion 10 located at the lateral end of the tube 1 is approximately the same as that of the flat wall portion 9.
  • each of the outermost unit passages 11a, 11a is formed to have a circumferentially smooth curved shape in cross-section. Therefore, a stress concentration on connecting portions between the outermost dividing wall 8 and the flat wall portion 9 decreases due to the stress concentration decreasing effect of the curved inner surfaces 12, 12, which prevents the peripheral wall 7 at the connecting portion from being damaged.
  • each intermediate unit passage 11 has a trapezoidal cross-sectional shape, the thickness of each portion can be thinner, thereby lightening the weight of the tube 1, resulting in a light weight heat exchanger, as in the same manner in the third embodiment. Further, the heat exchanging performance can be improved by the large contact area with a heat exchanging medium, as compared to a tube having intermediate unit passages each having a round shape in cross-section.
  • FIGS. 10 and 11 show a fifth embodiment of a multi-bored flat tube 1 according to the present invention.
  • This tube 1 is an aluminum extruded formed article as in the third and fourth embodiments.
  • the multi-bored flat tube 1 has a pair of outermost unit passages 11a, 11a and intermediate unit passages 11 therebetween.
  • Each intermediate unit passage 11 has a rectangular-based inner surface in cross-section having a plurality of triangular cross-sectional inner fins 15 continuously formed along the inner surface and extending in the longitudinal direction of the tube 1.
  • an inclined inner surface 16 is formed at each corner of the rectangular-based inner surface in cross-section.
  • each outermost unit passage 11a is formed to have a perfect circular shape.
  • the flat tube 1 has a plurality of inner fins 15 formed on the rectangular-based inner surface of the intermediate unit passage 11, a contact area with the heat exchanging medium can be increased, whereby a high heat exchanging performance can be obtained.
  • the flat tube 1 has a plurality of dividing walls 8 connecting the flat wall portions 9, 9, which divide the inner space of the tube 1 into a plurality of unit passages 11, 11a, thereby being superior in pressure resistance.
  • each of the outermost unit passages 11a, 11a is formed to have a circular shape in cross-section. Therefore, a stress concentration on connecting portions between the outermost dividing wall 8 and the flat wall portion 9 is decreased due to the stress concentration decreasing effect of the curved inner surfaces 12, 12, which prevents the peripheral wall 7 at the connecting portions from being damaged.
  • the outermost connecting portions are not sufficiently reinforced by the corrugate fins 2 as compared to the other connecting portions.
  • each outermost unit passage 11a is formed to have a circular shape in cross-section, a breakage of the connecting portions between the outermost dividing wall 8 and the flat wall portion 7 can be prevented due to the stress concentration diminishing effects, which in turn enhances inner pressure resistance performance of the tube 1.
  • the outermost unit passage 11a is formed to have a perfect circular shape, the inner pressure of the heat exchanging medium passing through the unit passage can be equalized on the inner surface of the outermost unit passage 11a, resulting in extremely high pressure performance.
  • each outermost unit passage 11a has a circular cross-sectional shape to decrease a stress concentration at the connecting portions between the outermost dividing wall 8 and the peripheral wall 7, even if a stone hits the tube, damage at the connecting portions and a breakage of the tube 1 can be effectively prevented.
  • each outermost unit passage 11a is formed to have a circular cross-sectional shape and each intermediate unit passage 11 has a rectangular-based cross-sectional shape, each portion of the tube 1 can be thin, which can lighten the weight of the tube 1, resulting in a light weight heat exchanger. Further, the heat transferring area can be kept larger, as compared to an intermediate unit passage having a circular cross-sectional shape. In addition, because each intermediate unit passage 11 has a plurality of inner fins 15, the heat transferring area can be increased, resulting in a high heat exchanging performance.
  • the thickness of the dividing wall 8 can be thin, which can lighten the weight of the tube 1 and enhance the pressure resistance of the tube 1.
  • the inclined inner surface 16 can enlarge the distance between the stress concentration portions A, A at the dividing walls 8 except for the outermost dividing wall 8. This decreases a stress concentration at the connecting portions between the dividing walls 8 and the peripheral wall 7.
  • a stress concentration at connecting portions between the outermost dividing wall 8 and the peripheral wall 7 can also be decreased because the outermost unit passage 11a has a circular cross-sectional shape with no stress concentration portion and the distance between the stress concentration portion A of the outer most dividing wall 8 and the central portion C of the outermost dividing wall 8 is large. Therefore, the tube 1 has a good pressure resistance. Because high pressure resistance is obtained by forming the inclined inner surfaces 16, the thickness of the dividing wall 8 can be thinner. As a result, a light weight tube can be obtained.
  • the weight of the tube 1 can be lighter where the pressure resistance remains the same, or the pressure resistance can be improved where the weight remains the same.
  • each outermost unit passage 11a has a perfect circular shape, however, it may have a circumferentially smooth curved shape in cross-section such as an elliptical shape or an elongated circular shape.
  • Continuously formed inner fins 15 each having a triangular cross-sectional shape are shown in the embodiment.
  • the inner fin may have various kinds of cross-sectional shapes.
  • the inner fin 15 may be formed on one of the dividing walls 8 or the peripheral walls 7, or may also be discontinuously formed.
  • FIGS. 12A-12B shows a sixth embodiment of a multi-bored flat tube 1 according to the present invention.
  • each outermost unit passage 11a is formed to be a circumferentially smooth curved shape in cross-section as in the same manner shown in the other embodiments.
  • Each intermediate unit passages 11 has a star-like shape, in detail, a circular-based inner surface in cross-section having a plurality of triangular cross-sectional inner fins 15 continuously formed along the inner surface and extending in the longitudinal direction of the tube 1.
  • the flat tube 1 has a plurality of inner fins 15 formed on the circular-based inner surface of the intermediate unit passage 11, the pressure resistance is good.
  • the contact area with the heat exchanging medium can be kept large, whereby a high heat exchanging performance can be obtained.
  • the flat tube 1 has a plurality of dividing walls 8 connecting the flat wall portions 9, 9, which divide the inner space of the tube 1 into a plurality of unit passages 11, 11a, thereby being superior in pressure resistance. Further, each outermost unit passage 11a is formed to have a circumferentially smooth curved shape in cross-section. Therefore, a stress concentration on connecting portions between the outermost dividing wall 8 and the flat wall portion 9 can be decreased, which prevents the peripheral wall 7 at the connecting portions from being destroyed.
  • each outermost unit passage 11a is formed to have a circumferentially smooth curved shape in cross-section, a breakage of the connecting portions between the outermost dividing wall 8 and the flat wall portion 7 can be prevented due to the stress concentration diminishing effects, which in turn enhances inner pressure resistance performance of the tube 1.
  • the outermost unit passage 11a is formed to have a perfect circular shape, the inner pressure of the heat exchanging medium passing through the unit passage 11a can be equalized on the inner surface of the outermost unit passage 11a, resulting in extremely high pressure performance.
  • each outermost unit passage 11a has a circumferentially smooth curved shape in cross-section to decrease stress concentration at the connecting portion between the outermost dividing wall 8 and the peripheral wall 7, even if a stone hits the tube, damage at the connecting portions and breakage of the tube 1 can be effectively prevented.
  • each outermost unit passage 11a has a perfect circular shape, however, it may have a circumferentially smooth curved shape in cross-section, such as an elliptical shape or an elongated circular shape.
  • Continuously formed inner fins 15 each having a triangular cross-sectional shape are shown in the embodiment.
  • the inner fin may have various kinds of cross-sectional shapes.
  • the inner fin 15 may also be discontinuously formed.
  • FIGS. 13A-13B show a seventh embodiment of a multi-bored flat tube according to the present invention. This embodiment differs from the sixth embodiment only in that the outermost unit passages 11a, 11a are also formed to have a star-like cross-sectional shape, respectively.
  • the flat tube 1 has a plurality of circular-based unit passages 11 including the outermost unit passages 11a, thereby being superior in pressure resistance.
  • a plurality of inner fins 15 are formed on the inner surface of all of the unit passages 11, 11a, the contact area with the heat exchanging medium can be increased, whereby a high heat exchanging performance can be obtained.
  • the flat tube 1 has a plurality of dividing walls 8 connecting the flat wall portions 9, 9, which divide the inner space of the tube 1 into a plurality of unit passages 11, 11a, thereby being superior in pressure resistance. Further, each outermost unit passage 11a is formed to have a circular-based cross-sectional shape. Therefore, a stress concentration on connecting portions between the outermost dividing wall 8 and the flat wall portion 9 is decreased, which prevents the peripheral wall 7 at the connecting portions from being destroyed.
  • each outermost unit passage 11a is formed to have a circular-based shape in cross-section, a breakage of the connecting portions connecting the outermost dividing wall 8 and the flat wall portion 7 can be prevented due to stress concentration diminishing effects, which in turn enhances inner pressure resistance performance of the tube 1 mounted in a heat exchanger.
  • each unit passage 11, 11a has a circular-based shape having a plurality of inner fins, however, it may have an elliptical-based shape or an elongated circular-based shape.
  • Continuously formed inner fins 15 each having a triangular cross-section are shown in the embodiment. However, the inner fin may have various kinds of cross-sectional shapes. Further, the inner fin 15 may also be discontinuously formed.
  • the flat tube according to the present invention is not limited to a tube for use in a condenser for an automobile air conditioner, and can be used as a tube for use in various kinds of heat exchangers such as, for example, an outdoor heat exchanger for a room air conditioner.
  • circular used herein is not limited to exact or perfect circles, but encompasses generally circle-like shapes, e.g., rounded shapes, but the most preferred embodiments having such shapes include perfect circles or substantially perfect circles.
  • rectangular, triangular, trapezoidal, elliptical, etc. is not limited to exact or perfect rectangles, triangles, trapezoids, ellipses, etc., but the most preferred embodiments having such shapes include exact or perfect shapes or substantially exact or perfect shapes.
  • the tubes are used in a multi-flow type heat exchanger.
  • the tubes may also be used in a serpentine type heat exchanger in which a tube is bent in a zigzag manner.
  • the outer fin disposed between adjacent tubes 1 is an corrugate fin, but is not limited to this.
  • the outermost unit passage has a circular-based inner surface in cross-section, a stress concentration on connecting portions between the outermost dividing wall and the peripheral wall can be decreased. Accordingly, a high pressure resistance can be obtained throughout the tube. In a heat-exchanger using the multi-bored flat tube, a high pressure resistance can be obtained by the structure even at both lateral ends of the tube where reinforcing effect by the outer fins is not enough.
  • a stress concentration on connecting portions between the outermost dividing wall and the peripheral wall can be reduced even when a small article such as a stone hits the tube. Consequently, the peripheral wall at the connecting portions can be prevented from being damaged, resulting in a superior breaking strength against an outside stress caused when a small article such as a stone hits the tube.
  • Each of the intermediate unit passages is designed to have a non-circular inner surface in cross-section. This can prevent the thickness of upper and lower portions of the dividing wall from being thickened, as compared to an intermediate unit passage having a circular-based inner surface, which results in a decreased amount of material forming the tube, thereby decreasing the weight and cost of the tube.
  • a larger contact area with the heat exchanging medium can be obtained as compared to an intermediate unit passage having a circular inner surface, which in turn can obtain a high heat exchanging performance.
  • a tube that has an outermost unit passage of a star-like shape in cross-section having a plurality of inner fins extending in a longitudinal direction of the tube, the same functions and effects can be obtained. Because a plurality of inner fins are formed on the inner surface of the outermost unit passage, a contact area with a heat exchanging medium in the outermost unit passage can be enlarged, thereby improving a heat exchange performance.
  • a stress concentration on the connecting portions between the outermost dividing wall and the peripheral wall can be decreased to improve the strength, whereby the peripheral wall at the connecting portions can effectively be prevented from being broken.
  • a sidewall portion has a rounded shape and is formed relatively thicker than the flat wall portions, the sidewall portion can be prevented from being broken or deformed when small article such as a stone hits the tube.
  • the thickness of the flat wall portions is kept relatively thin, an optimal heat transmission performance can be maintained and a weight increase can be decreased, resulting in a light-weight heat exchanger. Further, the structure does not cause an increase in the pressure loss of the heat exchanging medium.
  • a high performance of pressure-resistance and a large heat transmission area can be obtained by the intermediate unit passage having a circular-based cross-sectional shape with a plurality of inner fins extending in a longitudinal direction of the tube.
  • the intermediate unit passage may have a star-like shape in cross-section.
  • peripheral wall including flat wall portions facing with each other at a certain distance and sidewall portions connecting ends of the flat wall portions; and dividing walls connecting the flat wall portions and dividing an inside space defined by the peripheral wall to form a plurality of unit passages arranged in a lateral direction of the tube,
  • the plurality of unit passages include outermost unit passages located at both lateral ends of the tube and intermediate unit passages located between the outermost unit passages, and
  • each of the outermost unit passages has a circular-based inner surface in cross-section, and each of the intermediate unit passages has a modified cross-sectional shape.
  • a larger contact area with the heat exchanging medium can be obtained as compared to an intermediate unit passage having a circular inner surface in cross-section, which in turn can obtain a high heat exchanging performance.
  • a stress concentration on connecting portions between the outermost dividing wall and the peripheral wall can be reduced when a small article such as a stone hits the tube. Consequently, the peripheral wall at the connecting portions can be prevented from being damaged, resulting in superior breaking strength against an outside stress caused when a small article such as a stone hits the tube.
  • each intermediate unit passage has a rectangular-based shape having a plurality of inner fins extending in the longitudinal direction of the tube
  • the thickness of upper and lower portions of the dividing wall can be prevented from being thickened as compared to an intermediate unit passage having a circular-based inner surface, which results in a decreased amount of material, thereby decreasing the weight and cost of the tube.
  • a larger contact area with the heat exchanging medium can be obtained as compared to an intermediate unit passage having a circular inner surface, which in turn can obtain a high heat exchanging performance.
  • a heat exchanger including the above-mentioned multi-bored flat tubes has an improved strength against a stone which hits the tube, an excellent heat exchanging performance, and a low pressure loss.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US09/087,016 1997-05-30 1998-05-29 Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes Expired - Fee Related US6000467A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US09/419,519 US6289981B1 (en) 1997-05-30 1999-10-18 Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP9-142017 1997-05-30
JP14201797 1997-05-30
JP10-069957 1998-03-19
JP10069957A JPH1144498A (ja) 1997-05-30 1998-03-19 熱交換器用偏平多孔チューブ及び同チューブを用いた熱交換器

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US09/419,519 Division US6289981B1 (en) 1997-05-30 1999-10-18 Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes

Publications (1)

Publication Number Publication Date
US6000467A true US6000467A (en) 1999-12-14

Family

ID=26411135

Family Applications (2)

Application Number Title Priority Date Filing Date
US09/087,016 Expired - Fee Related US6000467A (en) 1997-05-30 1998-05-29 Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes
US09/419,519 Expired - Lifetime US6289981B1 (en) 1997-05-30 1999-10-18 Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes

Family Applications After (1)

Application Number Title Priority Date Filing Date
US09/419,519 Expired - Lifetime US6289981B1 (en) 1997-05-30 1999-10-18 Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes

Country Status (8)

Country Link
US (2) US6000467A (de)
EP (1) EP0881448B1 (de)
JP (1) JPH1144498A (de)
AT (1) ATE262153T1 (de)
AU (1) AU735895B2 (de)
CZ (1) CZ298149B6 (de)
DE (1) DE69822361T2 (de)
ES (1) ES2216205T3 (de)

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6189607B1 (en) * 1998-07-31 2001-02-20 Kazuki Hosoya Heat exchanger
US6241012B1 (en) * 1999-12-10 2001-06-05 Visteon Global Technologies, Inc. Folded tube for a heat exchanger and method of making same
US6302195B1 (en) * 1999-02-15 2001-10-16 Nissan Motor Co., Ltd. Heat exchanger
US6357522B2 (en) * 1998-10-01 2002-03-19 Behr Gmbh & Co. Multi-channel flat tube
US20030066636A1 (en) * 2001-10-09 2003-04-10 Masaaki Kawakubo Tube and heat exchanger having the same
US20040099946A1 (en) * 2002-11-27 2004-05-27 Dickey James Todd High density electronic cooling triangular shaped microchannel device
US20040134226A1 (en) * 2001-06-14 2004-07-15 Kraay Michael L. Condenser for air cooled chillers
US20040251013A1 (en) * 2003-05-23 2004-12-16 Masaaki Kawakubo Heat exchange tube having multiple fluid paths
US6854512B2 (en) * 2002-01-31 2005-02-15 Halla Climate Control Corporation Heat exchanger tube and heat exchanger using the same
US6880627B2 (en) * 1999-12-09 2005-04-19 Denso Corporation Refrigerant condenser used for automotive air conditioner
US20050269069A1 (en) * 2004-06-04 2005-12-08 American Standard International, Inc. Heat transfer apparatus with enhanced micro-channel heat transfer tubing
US20050274506A1 (en) * 2004-06-14 2005-12-15 Bhatti Mohinder S Flat tube evaporator with enhanced refrigerant flow passages
US20060151160A1 (en) * 2002-10-02 2006-07-13 Showa Denko K.K. Heat exchanging tube and heat exchanger
US20060278365A1 (en) * 2004-06-10 2006-12-14 Ryouichi Sanada Cooling system used for hybrid-powered automobile
US20070071920A1 (en) * 2005-09-29 2007-03-29 Denso Corporation Heat exchanger tube and heat exchanger
US20080185130A1 (en) * 2007-02-07 2008-08-07 Behr America Heat exchanger with extruded cooling tubes
CN100455969C (zh) * 2002-12-31 2009-01-28 穆丹韩国有限会社 蒸发器
US20090188110A1 (en) * 2002-09-03 2009-07-30 Seok Hwan Moon Micro heat pipe with poligonal cross-section manufactured via extrusion or drawing
US20100089546A1 (en) * 2008-10-09 2010-04-15 Gm Global Technology Operations, Inc. Vehicle heat exchangers having shielding channels
US20120267086A1 (en) * 2008-08-28 2012-10-25 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US20130111945A1 (en) * 2010-05-31 2013-05-09 Naotaka Iwasawa Heat Exchanger and Heat Pump Using Same
US20130306280A1 (en) * 2012-05-18 2013-11-21 Delphi Technologies, Inc. Heat exchanger having a condensate extractor
US20140262174A1 (en) * 2011-10-19 2014-09-18 Ws-Warmprozesstechnik Gmbh Et Al. High-Temperature Heat Exchanger
US20140290924A1 (en) * 2011-09-15 2014-10-02 Patrick Gilbert Conduit assemblies for heat exchangers and the like
US20150237872A1 (en) * 2012-09-14 2015-08-27 Revent International Ab Hot air oven
USD763417S1 (en) * 2012-08-02 2016-08-09 Mitsubishi Electric Corporation Heat exchanger tube
US20200088474A1 (en) * 2018-09-13 2020-03-19 Denso International America, Inc. Impact resistant structural radiator tube
US20210239408A1 (en) * 2020-02-03 2021-08-05 Hamilton Sundstrand Corporation Evaporator with grooved channels
US11156592B2 (en) * 2018-06-11 2021-10-26 Gemological Institute Of America, Inc. (Gia) Upflow cooling stage for photoluminescence analysis
US20210358833A1 (en) * 2020-05-14 2021-11-18 Lite-On Semiconductor Corporation Direct cooling power semiconductor package
CN114729793A (zh) * 2019-11-14 2022-07-08 大金工业株式会社 传热管以及热交换器
US11395497B2 (en) 2010-03-04 2022-07-26 Revent International Ab Device for baking dough-based food products, net and method for baking such products
USD982730S1 (en) * 2019-06-18 2023-04-04 Caterpillar Inc. Tube

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5979440A (en) * 1997-06-16 1999-11-09 Sequal Technologies, Inc. Methods and apparatus to generate liquid ambulatory oxygen from an oxygen concentrator
JP2000074587A (ja) * 1998-08-27 2000-03-14 Zexel Corp 熱交換器
DE50110536D1 (de) 2000-11-01 2006-09-07 Akg Thermotechnik Gmbh & Co Kg Wärmeaustauscher, insbesondere für Kondensations-Wäschetrockner
DE10054158A1 (de) * 2000-11-02 2002-05-08 Behr Gmbh Mehrkammerrohr mit kreisförmigen Strömungskanälen
JP2008224213A (ja) * 2001-06-18 2008-09-25 Showa Denko Kk 蒸発器
US20040112572A1 (en) * 2002-12-17 2004-06-17 Moon Seok Hwan Micro heat pipe with poligonal cross-section manufactured via extrusion or drawing
GB2399623A (en) 2003-03-19 2004-09-22 Calsonic Kansei Uk Ltd Flat tube heat exchanger for a vehicle air conditioning system
US7559355B2 (en) 2003-06-20 2009-07-14 Halla Climate Control Corporation Tube for heat exchanger
JP4679827B2 (ja) * 2003-06-23 2011-05-11 株式会社デンソー 熱交換器
JP2005315467A (ja) * 2004-04-27 2005-11-10 Denso Corp 熱交換器
CN100592017C (zh) * 2005-02-02 2010-02-24 开利公司 微流道扁平管式热交换器
JP4898300B2 (ja) * 2006-05-30 2012-03-14 昭和電工株式会社 エバポレータ
JP5276807B2 (ja) * 2007-07-17 2013-08-28 株式会社ケーヒン・サーマル・テクノロジー 熱交換器
US20090159253A1 (en) * 2007-12-21 2009-06-25 Zaiqian Hu Heat exchanger tubes and combo-coolers including the same
JP5187047B2 (ja) * 2008-07-29 2013-04-24 株式会社デンソー 熱交換器用チューブ
JP5393514B2 (ja) * 2010-02-04 2014-01-22 臼井国際産業株式会社 熱交換器
JP5622414B2 (ja) * 2010-03-29 2014-11-12 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
FR2968754B1 (fr) * 2010-12-10 2014-10-10 Valeo Systemes Thermiques Tube d'echangeur de chaleur, echangeur de chaleur comportant de tels tubes et procede d'obtention d'un tel tube.
US9017027B2 (en) * 2011-01-06 2015-04-28 Siemens Energy, Inc. Component having cooling channel with hourglass cross section
US8764394B2 (en) 2011-01-06 2014-07-01 Siemens Energy, Inc. Component cooling channel
CN102269536A (zh) * 2011-08-17 2011-12-07 三花丹佛斯（杭州）微通道换热器有限公司 用于换热器的扁管以及具有该扁管的换热器
US9151173B2 (en) * 2011-12-15 2015-10-06 General Electric Company Use of multi-faceted impingement openings for increasing heat transfer characteristics on gas turbine components
CN104145169A (zh) * 2012-02-24 2014-11-12 株式会社Uacj 翅片管式换热器用传热管和使用了其的翅片管式换热器
CN104380026A (zh) * 2012-06-13 2015-02-25 株式会社Uacj 翅片管式换热器用传热管和使用了其的翅片管式换热器
JP6194700B2 (ja) * 2013-08-30 2017-09-13 富士通株式会社 放熱器および放熱器の製造方法
DE102014213088A1 (de) 2014-07-04 2016-01-07 Mahle International Gmbh Flachrohr
US9995151B2 (en) 2015-08-17 2018-06-12 General Electric Company Article and manifold for thermal adjustment of a turbine component
DE102017201081A1 (de) * 2016-01-25 2017-07-27 Hanon Systems Rohr für einen Wärmetauscher
US10451360B2 (en) 2016-10-24 2019-10-22 Hamilton Sundstrand Corporation Heat exchanger with integral anti-icing
US11002386B2 (en) * 2019-01-17 2021-05-11 Fmc Technologies, Inc. Low erosion fluid conduit with sharp section geometry
DE102019217368A1 (de) * 2019-11-11 2021-05-12 Mahle International Gmbh Rohrkörper für einen Wärmeübertrager sowie Wärmeübertrager

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB363083A (en) * 1930-11-10 1931-12-17 Georg Franz Holler Improvements in, or relating to, economisers or other tubular heat exchangers
FR69269E (fr) * 1956-02-08 1958-10-23 Georgsmarienwerke Ag Châssis de porte refroidi, pour fours industriels
GB2133525A (en) * 1983-01-10 1984-07-25 Nippon Denso Co Heat exchange tube
JPS6391492A (ja) * 1986-10-03 1988-04-22 Nippon Denso Co Ltd 熱交換器
US5251692A (en) * 1991-06-20 1993-10-12 Thermal-Werke Warme-, Kalte-, Klimatechnik Gmbh Flat tube heat exchanger, method of making the same and flat tubes for the heat exchanger

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5942615Y2 (ja) * 1980-10-16 1984-12-13 株式会社デンソー 蒸発器
JPS5971083U (ja) * 1982-10-27 1984-05-14 昭和アルミニウム株式会社 熱交換器用管
JPS63116095A (ja) * 1986-10-31 1988-05-20 Matsushita Refrig Co 偏平熱交換器管
JPH02230091A (ja) * 1989-03-01 1990-09-12 Hitachi Ltd サーペンタイン形熱交換器
US5009262A (en) * 1990-06-19 1991-04-23 General Motors Corporation Combination radiator and condenser apparatus for motor vehicle
JP2990947B2 (ja) 1991-12-09 1999-12-13 株式会社デンソー 冷媒凝縮器
US5307870A (en) * 1991-12-09 1994-05-03 Nippondenso Co., Ltd. Heat exchanger
JPH06185885A (ja) * 1992-07-24 1994-07-08 Furukawa Electric Co Ltd:The 偏平多穴凝縮伝熱管
JP3617561B2 (ja) 1995-11-27 2005-02-09 株式会社リコー 画像形成方法及びその装置
JPH1069957A (ja) 1996-08-29 1998-03-10 Furukawa Electric Co Ltd:The 回転コネクタ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB363083A (en) * 1930-11-10 1931-12-17 Georg Franz Holler Improvements in, or relating to, economisers or other tubular heat exchangers
FR69269E (fr) * 1956-02-08 1958-10-23 Georgsmarienwerke Ag Châssis de porte refroidi, pour fours industriels
GB2133525A (en) * 1983-01-10 1984-07-25 Nippon Denso Co Heat exchange tube
JPS6391492A (ja) * 1986-10-03 1988-04-22 Nippon Denso Co Ltd 熱交換器
US5251692A (en) * 1991-06-20 1993-10-12 Thermal-Werke Warme-, Kalte-, Klimatechnik Gmbh Flat tube heat exchanger, method of making the same and flat tubes for the heat exchanger

Cited By (54)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6189607B1 (en) * 1998-07-31 2001-02-20 Kazuki Hosoya Heat exchanger
US6357522B2 (en) * 1998-10-01 2002-03-19 Behr Gmbh & Co. Multi-channel flat tube
US6302195B1 (en) * 1999-02-15 2001-10-16 Nissan Motor Co., Ltd. Heat exchanger
US6880627B2 (en) * 1999-12-09 2005-04-19 Denso Corporation Refrigerant condenser used for automotive air conditioner
US20050155747A1 (en) * 1999-12-09 2005-07-21 Ryouichi Sanada Refrigerant condenser used for automotive air conditioner
US7140424B2 (en) 1999-12-09 2006-11-28 Denso Corporation Refrigerant condenser used for automotive air conditioner
US6241012B1 (en) * 1999-12-10 2001-06-05 Visteon Global Technologies, Inc. Folded tube for a heat exchanger and method of making same
US20040134226A1 (en) * 2001-06-14 2004-07-15 Kraay Michael L. Condenser for air cooled chillers
US20030066636A1 (en) * 2001-10-09 2003-04-10 Masaaki Kawakubo Tube and heat exchanger having the same
US6935414B2 (en) * 2001-10-09 2005-08-30 Denso Corporation Tube and heat exchanger having the same
US6854512B2 (en) * 2002-01-31 2005-02-15 Halla Climate Control Corporation Heat exchanger tube and heat exchanger using the same
US20090188110A1 (en) * 2002-09-03 2009-07-30 Seok Hwan Moon Micro heat pipe with poligonal cross-section manufactured via extrusion or drawing
US20070074862A1 (en) * 2002-10-02 2007-04-05 Showa Denko K.K. Heat exchanging tube and heat exchanger
US7165606B2 (en) * 2002-10-02 2007-01-23 Showa Denko K.K. Heat exchanging tube and heat exchanger
US20060151160A1 (en) * 2002-10-02 2006-07-13 Showa Denko K.K. Heat exchanging tube and heat exchanger
US20040099946A1 (en) * 2002-11-27 2004-05-27 Dickey James Todd High density electronic cooling triangular shaped microchannel device
US20060011334A1 (en) * 2002-11-27 2006-01-19 The Aerospace Corp. High density electronic cooling triangular shaped microchannel device
US6983792B2 (en) * 2002-11-27 2006-01-10 The Aerospace Corporation High density electronic cooling triangular shaped microchannel device
US7523780B2 (en) * 2002-11-27 2009-04-28 The Aerospace Corporation High density electronic cooling triangular shaped microchannel device
CN100455969C (zh) * 2002-12-31 2009-01-28 穆丹韩国有限会社 蒸发器
US7849915B2 (en) * 2003-05-23 2010-12-14 Denso Corporation Heat exchange tube having multiple fluid paths
US20040251013A1 (en) * 2003-05-23 2004-12-16 Masaaki Kawakubo Heat exchange tube having multiple fluid paths
US20050269069A1 (en) * 2004-06-04 2005-12-08 American Standard International, Inc. Heat transfer apparatus with enhanced micro-channel heat transfer tubing
US20060278365A1 (en) * 2004-06-10 2006-12-14 Ryouichi Sanada Cooling system used for hybrid-powered automobile
US7080683B2 (en) * 2004-06-14 2006-07-25 Delphi Technologies, Inc. Flat tube evaporator with enhanced refrigerant flow passages
US20050274506A1 (en) * 2004-06-14 2005-12-15 Bhatti Mohinder S Flat tube evaporator with enhanced refrigerant flow passages
US20070071920A1 (en) * 2005-09-29 2007-03-29 Denso Corporation Heat exchanger tube and heat exchanger
US20080185130A1 (en) * 2007-02-07 2008-08-07 Behr America Heat exchanger with extruded cooling tubes
US8938988B2 (en) * 2008-08-28 2015-01-27 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US20120267086A1 (en) * 2008-08-28 2012-10-25 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US20100089546A1 (en) * 2008-10-09 2010-04-15 Gm Global Technology Operations, Inc. Vehicle heat exchangers having shielding channels
US11395497B2 (en) 2010-03-04 2022-07-26 Revent International Ab Device for baking dough-based food products, net and method for baking such products
US9127868B2 (en) * 2010-05-31 2015-09-08 Sanden Corporation Heat exchanger and a heat pump using same
US20130111945A1 (en) * 2010-05-31 2013-05-09 Naotaka Iwasawa Heat Exchanger and Heat Pump Using Same
US20140290924A1 (en) * 2011-09-15 2014-10-02 Patrick Gilbert Conduit assemblies for heat exchangers and the like
US10914528B2 (en) * 2011-10-19 2021-02-09 Ws-Warmeprozesstechnik Gmbh High-temperature heat exchanger
US20140262174A1 (en) * 2011-10-19 2014-09-18 Ws-Warmprozesstechnik Gmbh Et Al. High-Temperature Heat Exchanger
CN104285108A (zh) * 2012-05-18 2015-01-14 德尔福技术有限公司 具有冷凝物抽取器的热交换器
CN104285108B (zh) * 2012-05-18 2017-05-31 马勒国际有限公司 具有冷凝物抽取器的热交换器
US9909818B2 (en) * 2012-05-18 2018-03-06 Mahle International Gmbh Heat exchanger having a condensate extractor
US20130306280A1 (en) * 2012-05-18 2013-11-21 Delphi Technologies, Inc. Heat exchanger having a condensate extractor
USD763417S1 (en) * 2012-08-02 2016-08-09 Mitsubishi Electric Corporation Heat exchanger tube
US20150237872A1 (en) * 2012-09-14 2015-08-27 Revent International Ab Hot air oven
US10258049B2 (en) * 2012-09-14 2019-04-16 Revent International Ab Hot air oven
US11543401B2 (en) 2018-06-11 2023-01-03 Gemological Institute Of America, Inc. (Gia) Upflow cooling stage for photoluminescence analysis
US11156592B2 (en) * 2018-06-11 2021-10-26 Gemological Institute Of America, Inc. (Gia) Upflow cooling stage for photoluminescence analysis
US20200088474A1 (en) * 2018-09-13 2020-03-19 Denso International America, Inc. Impact resistant structural radiator tube
USD982730S1 (en) * 2019-06-18 2023-04-04 Caterpillar Inc. Tube
CN114729793A (zh) * 2019-11-14 2022-07-08 大金工业株式会社 传热管以及热交换器
EP4060252A4 (de) * 2019-11-14 2022-12-07 Daikin Industries, Ltd. Wärmeübertragungsrohr für wärmetauscher
CN114729793B (zh) * 2019-11-14 2024-04-02 大金工业株式会社 传热管以及热交换器
US20210239408A1 (en) * 2020-02-03 2021-08-05 Hamilton Sundstrand Corporation Evaporator with grooved channels
US11808528B2 (en) * 2020-02-03 2023-11-07 Hamilton Sundstrand Corporation Evaporator with grooved channels and orifice inserts
US20210358833A1 (en) * 2020-05-14 2021-11-18 Lite-On Semiconductor Corporation Direct cooling power semiconductor package

Also Published As

Publication number Publication date
CZ298149B6 (cs) 2007-07-04
AU6980198A (en) 1998-12-03
AU735895B2 (en) 2001-07-19
JPH1144498A (ja) 1999-02-16
DE69822361D1 (de) 2004-04-22
EP0881448B1 (de) 2004-03-17
ATE262153T1 (de) 2004-04-15
CZ169698A3 (cs) 2000-08-16
DE69822361T2 (de) 2005-02-17
ES2216205T3 (es) 2004-10-16
US6289981B1 (en) 2001-09-18
EP0881448A3 (de) 1999-11-24
EP0881448A2 (de) 1998-12-02

Similar Documents

Publication Publication Date Title
US6000467A (en) Multi-bored flat tube for use in a heat exchanger and heat exchanger including said tubes
US4300629A (en) Cross-fin tube type heat exchanger
JP4347961B2 (ja) 多路扁平管
US6209202B1 (en) Folded tube for a heat exchanger and method of making same
US5372188A (en) Heat exchanger for a refrigerant system
US5329988A (en) Heat exchanger
JP3962798B2 (ja) 達磨型流路を有する熱交換器用チューブ及びこれを用いた熱交換器
EP0860674B1 (de) Wärmetauscher
US8276652B2 (en) High performance louvered fin for heat exchanger
US7182127B2 (en) Heat exchanger
US6209628B1 (en) Heat exchanger having several heat exchanging portions
US5458190A (en) Condenser
EP2175223A1 (de) Kühlverdampfer
US4715437A (en) Heat exchanger
JP5716499B2 (ja) 熱交換器及び空気調和機
JPH06221787A (ja) 熱交換器
US5170842A (en) Fin-tube type heat exchanger
US20030094260A1 (en) Heat exchanger tube with stone protection appendage
AU710016B2 (en) A heat exchanger for an air conditioner or the like
US6739387B1 (en) Heat exchanger tubing and heat exchanger assembly using said tubing
JP3430909B2 (ja) 空気調和機
JPH06129734A (ja) 熱交換器
CN210051023U (zh) 换热器和空调器
JP4513207B2 (ja) 空気熱交換器
JPH0410530Y2 (de)

Legal Events

Date Code Title Description
AS Assignment

Owner name: SHOWA ALUMINUM CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TOKIZAKI, KAZUMI;HIGO, YUTAKA;GO, NOBUAKI;AND OTHERS;REEL/FRAME:009230/0198

Effective date: 19980527

AS Assignment

Owner name: SHOWA DENKO K.K., JAPAN

Free format text: MERGER;ASSIGNOR:SHOWA ALUMINUM CORPORATION;REEL/FRAME:011887/0720

Effective date: 20010330

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 4

FPAY Fee payment

Year of fee payment: 8

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

FP Lapsed due to failure to pay maintenance fee

Effective date: 20111214